CN102032699B - Refrigeration cycle apparatus and hot water heater - Google Patents
Refrigeration cycle apparatus and hot water heater Download PDFInfo
- Publication number
- CN102032699B CN102032699B CN201010539415.8A CN201010539415A CN102032699B CN 102032699 B CN102032699 B CN 102032699B CN 201010539415 A CN201010539415 A CN 201010539415A CN 102032699 B CN102032699 B CN 102032699B
- Authority
- CN
- China
- Prior art keywords
- heat exchanger
- cold
- producing medium
- condenser
- supercooling heat
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B40/00—Subcoolers, desuperheaters or superheaters
- F25B40/02—Subcoolers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B13/00—Compression machines, plants or systems, with reversible cycle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2339/00—Details of evaporators; Details of condensers
- F25B2339/04—Details of condensers
- F25B2339/047—Water-cooled condensers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/13—Economisers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2600/00—Control issues
- F25B2600/25—Control of valves
- F25B2600/2509—Economiser valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2101—Temperatures in a bypass
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2700/00—Sensing or detecting of parameters; Sensors therefor
- F25B2700/21—Temperatures
- F25B2700/2103—Temperatures near a heat exchanger
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Pump Type And Storage Water Heaters (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
The invention provides a refrigeration cycle apparatus capable of achieving high efficiency in high heating load running when the outside temperature is low, and a hot water heater using the refrigeration cycle apparatus. A refrigeration cycle apparatus 1 includes: a refrigerant circuit 2 including a condenser 22 and a subcooling heat exchanger 23; and a bypass passage 3 that extends through the subcooling heat exchanger 23. In the bypass passage 3, a dryness fraction of the refrigerant that has flowed out of the subcooling heat exchanger 23 is adjusted. Since the subcooling heat exchanger 23 is configured appropriately, a ratio of an amount of heat exchange between, in the bypass passage 3, the refrigerant decompressed by the bypass expansion means 31 and the refrigerant passing through the refrigerant circuit 2 with respect to an amount of heat exchange between, in the condenser 22, the refrigerant that has flowed into the condenser 22 and a fluid to be heated falls in a specified range even during the operation using the adjusted dryness fraction. As a result, the subcooling effect of the subcooling heat exchanger 23 is secured.
Description
Technical field
The plumbing fixture that the present invention relates to make the overcooled freezing cycle device of cold-producing medium and used this freezing cycle device.
Background technology
In the past, known freezing cycle device was provided with supercooling heat exchanger in the downstream of the condenser of refrigerant loop, by making the cold-producing medium expanding flow into this supercooling heat exchanger, the cold-producing medium that flows out condenser was carried out to supercooling.For example, in patent documentation 1, disclosed freezing cycle device 100 as shown in Figure 6.
This freezing cycle device 100 is provided with the refrigerant loop 110, the bypass flow path 120 that make refrigerant circulation.The structure of refrigerant loop 110 is: by pipe arrangement, with loop connecting compressor 111, condenser 112, supercooling heat exchanger 113, main expansion valve 114 and evaporimeter 115.Bypass flow path 120, between condenser 112 and supercooling heat exchanger 113, from refrigerant loop 110 branches, and is connected with refrigerant loop 110 between evaporimeter 115 and compressor 111 through cooling heat exchanger 113.In addition, in bypass flow path 120, be provided with bypass expansion valve 121 at the upstream side of supercooling heat exchanger 113.
In patent documentation 1, record the raising in order to realize refrigerating capacity, controlled bypass expansion valve 121 and reach the scope more than 1% and below 25% so that flow through the bypass refrigerant flow of bypass flow path 120 with the ratio (by-pass ratio) of the whole refrigerant flows that flow through condenser 112.
Patent documentation 1: No. 4036288 communique of Japanese Patent
Summary of the invention
But, realize high-efficiency operation in described freezing cycle device time, in supercooling heat exchanger, the refrigerant superheat of the bypass flow path that preferably do not make to flow through, and, preferably by the cold-producing medium supercooling of the refrigerant loop of flowing through to specified states.In the time realizing this situation, must suitably form supercooling heat exchanger.With regard to this point, in patent documentation 1, there is no to record especially the structure of supercooling heat exchanger.
The present invention be directed to that this situation makes, its object is to provide the plumbing fixture that is provided with the freezing cycle device that the supercooling heat exchanger that forms in a suitable manner can high-efficiency operation and has used this freezing cycle device.
The present inventor found that according to wholwe-hearted research: if the mass dryness fraction of cold-producing medium flowing out from supercooling heat exchanger is remained in bypass flow path more than 0.8 but less than 1.0 can obtain high COP (coefficient of performance).But, in the case of the mode control mass dryness fraction with within the scope of this, due to the capacity of supercooling heat exchanger, when the heating efficiency that lower and condenser requires at extraneous gas temperature increases, exist the supercooling of cold-producing medium of the refrigerant loop of flowing through insufficient or superfluous.The present invention is set out and is made by this viewpoint.
That is, the invention provides freezing cycle device, it is provided with: with the refrigerant loop of loop connecting compressor, condenser, supercooling heat exchanger, main expansion gear and evaporimeter; Bypass flow path, it is between described supercooling heat exchanger and described main expansion gear or between described condenser and described supercooling heat exchanger, from described refrigerant loop branch, and through described supercooling heat exchanger, between described evaporimeter and described compressor, be connected with described refrigerant loop; Be arranged on the bypass expansion gear that is positioned at described supercooling heat exchanger upstream side in described bypass flow path, described supercooling heat exchanger is when adjusting the aperture of described bypass expansion gear so that the mass dryness fraction of the cold-producing medium flowing out from this supercooling heat exchanger reaches more than 0.8 when less than 1.0 in described bypass flow path, in described supercooling heat exchanger, is more than 0.2 but below 0.8 by the cold-producing medium of described bypass expansion gear decompression and heat exchange amount between the cold-producing medium of described condenser outflow with respect to the ratio that flows into the heat exchange amount between cold-producing medium and the heated fluid of this condenser described condenser.
The present invention also provides plumbing fixture, and its device for utilizing the hot water being generated by heater to heat, is provided with freezing cycle device as this device of described heater.
As mentioned above, because supercooling heat exchanger has adopted suitable structure, therefore, in bypass flow path, the mass dryness fraction of cold-producing medium flowing out from supercooling heat exchanger is remained on more than 0.8 but when less than 1.0, even if the heating efficiency that ambient atmos temperature is lower and condenser requires increases, still can carry out supercooling to the cold-producing medium of the refrigerant loop of flowing through with the state being applicable to.Therefore,, according to the present invention, can realize high-efficiency operation.
Brief description of the drawings
Fig. 1 has shown the summary structure chart of the freezing cycle device that relates to one embodiment of the invention.
Fig. 2 is the graph of a relation at the mass dryness fraction of the cold-producing medium of evaporator inlet and heat exchange ratio, (a) has shown the situation as cold-producing medium by R407C, (b) has shown the situation as cold-producing medium by R410A.
Fig. 3 is that the not rel line chart (a) of the freezing cycle device when the cold-producing medium by R407C has shown in the mass dryness fraction of the cold-producing medium of the porch of evaporimeter to be the situation of 0.55 o'clock, (b) has shown in the mass dryness fraction of the cold-producing medium of the porch of evaporimeter to be the situation of 0 o'clock.
Fig. 4 is the not rel line chart of freezing cycle device when R410A is used as to cold-producing medium, (a) shown in the mass dryness fraction of the cold-producing medium of the porch of evaporimeter to be the situation of 0.45 o'clock, (b) shown in the mass dryness fraction of the cold-producing medium of the porch of evaporimeter to be the situation of 0 o'clock.
Fig. 5 is the graph of a relation under every kind of condensation temperature of cold-producing medium in condenser of ambient atmos temperature and heat exchange ratio.
Fig. 6 has shown the overview structure chart of freezing cycle device in the past.
Symbol description
1 freezing cycle device
2 refrigerant loops
21 compressors
22 condensers
23 supercooling heat exchangers
24 main expansion valves (main expansion gear)
25 evaporimeters
3 bypass flow path
31 bypass expansion valves (bypass expansion gear)
4 control device
61 inlet temperature sensors
62 outlet temperature sensors
Detailed description of the invention
Fig. 1 has shown the freezing cycle device 1 of one embodiment of the invention.This freezing cycle device 1 is provided with the refrigerant loop 2, bypass flow path 3 and the control device 4 that make refrigerant circulation.As cold-producing medium, for example, can adopt the accurate azeotropic refrigerant of mixed non-azeotropic refrigerant, the R410A etc. such as R407C or unitary system cryogen etc.
By pipe arrangement, with loop connecting compressor 21, condenser 22, supercooling heat exchanger 23, main expansion valve 24 and evaporimeter 25, thereby form refrigerant loop 2.In the present embodiment, between evaporimeter 25 and compressor 21, be provided with the secondary reservoir 26 and the main reservoir 27 that carry out gas-liquid separation.In addition, in refrigerant loop 2, be provided with the cross valve 28 for changing conventional running and defrosting running.
In the present embodiment, freezing cycle device 1 forms warm water that heater the is generated heater for the plumbing fixture that heats, and condenser 22 is formed on and between cold-producing medium and water, carries out heat exchange the heat exchanger to water heating.Specifically, supply pipe 71 is connected with recovery tube 72 with condenser 22, supplies water to condenser 22 by supply pipe 71, to reclaim the water (hot water) being heated by condenser 22 by recovery tube 72.For example, directly or by storage hot-tub etc., the water being reclaimed by recovery tube 72 (hot water) is sent in the heating installations such as radiator, heated thus.
Bypass flow path 3 is between supercooling heat exchanger 23 and main expansion valve 24, from refrigerant loop 2 branches, and through supercooling heat exchanger 23, be connected with refrigerant loop 2 between evaporimeter 25 and compressor 21.In the present embodiment, between secondary reservoir 26 and main reservoir 27, bypass flow path 3 is connected with refrigerant loop 2.In addition, in bypass flow path 3, at the upstream side of supercooling heat exchanger 23, bypass expansion valve 31 is set.
In routine running, by cross valve 28, the cold-producing medium of discharging from compressor 21 is sent into condenser 22; In defrosting running, by cross valve 28, the cold-producing medium of discharging from compressor 21 is sent into evaporimeter 25.In Fig. 1, the flow direction of cold-producing medium while having shown conventional running with arrow.Below, the state variation of the cold-producing medium in routine running is described.
The high-pressure refrigerant of discharging from compressor 21 flows into condenser 22, and to passing through the water heat release of condenser 22.The high-pressure refrigerant flowing out from condenser 22 flows into supercooling heat exchanger 23, and by the low pressure refrigerant being reduced pressure by bypass expansion valve 31, it is carried out to supercooling.The high-pressure refrigerant flowing out from supercooling heat exchanger 23 is to main expansion valve 24 sides and the 31 side shuntings of bypass expansion valve.
After by main expansion valve 24 puffings, flow into evaporimeter 25 to the high-pressure refrigerant of main expansion valve 24 sides shuntings.Flow into the low pressure refrigerant of evaporimeter 25 herein, from air, absorb heat.On the other hand, after by bypass expansion valve 31 puffings, flow into supercooling heat exchanger 23 to the high-pressure refrigerant of expansion valve 31 sides shuntings.The low pressure refrigerant that flows into supercooling heat exchanger 23 is heated by the high-pressure refrigerant flowing out from condenser 23.Afterwards, the low pressure refrigerant flowing out from supercooling heat exchanger 23 converges with the low pressure refrigerant flowing out from evaporimeter 25, and is again inhaled into compressor 21.
The structure of the freezing cycle device 1 of the present embodiment reduces and circulating mass of refrigerant minimizing for preventing the refrigerant pressure that is inhaled into compressor 21 in the time of low ambient atmos temperature, causes thus the heating efficiency of condenser 22 to reduce.Realizing in this structure, importantly: the enthalpy difference that increases evaporimeter 25 by supercooling, simultaneously, make refrigerant bypass by bypass flow path 3, thereby the amount of the vapor phase refrigerant that the endothermic effect of low-pressure side part of the refrigerant loop 2 that suppresses to flow through is less, reduces the pressure loss of the low-pressure side part of refrigerant loop 2 thus.If be reduced in the pressure loss of the low-pressure side part that reduces refrigerant loop 2, owing to being inhaled into, the refrigerant pressure of compressor 21 rises so that specific volume reduces, and therefore, circulating mass of refrigerant increases.In addition, if increase the enthalpy difference of evaporimeter 25, even if the mass flow of the cold-producing medium by evaporimeter 25 reduces because of bypass, still can guarantee the caloric receptivity of evaporimeter 25.,, if adjust cold-producing medium supercooling degree and bypass amount, the effect of heating efficiency raising and the COP of freezing cycle device 1 that can obtain condenser 22 improve effect simultaneously.
In the present embodiment, the design of supercooling heat exchanger 23 is: when adjusting the aperture of main expansion valve 24 and bypass expansion valve 31 so that the mass dryness fraction of the cold-producing medium flowing out from supercooling heat exchanger 23 reaches more than 0.8 when less than 1.0 in bypass flow path 3, the ratio (being heat exchange ratio) that has the heat exchange amount Qsc between the cold-producing medium being reduced pressure by bypass expansion valve 31 in supercooling heat exchanger 23 and the cold-producing medium flowing out from condenser 23 and flow into the heat exchange amount Qc between cold-producing medium and the water of condenser 22 condenser 22 reaches more than 0.2 but heat-conducting area below 0.8.
According to this structure, owing to suitably having set the heat-conducting area of supercooling heat exchanger 23, therefore, when guaranteeing in bypass flow path 3 that the mass dryness fraction of the cold-producing medium flowing out from supercooling heat exchanger 23 reaches more than 0.8 but when less than 1.0, even if the heating efficiency that ambient atmos temperature is lower and condenser 22 requires increases, still can carry out supercooling to the cold-producing medium of the refrigerant loop 2 of flowing through with suitable state.
For example, in the situation that adopting R407C as cold-producing medium, if at extraneous gas temperature AT=-25 DEG C, under the condition of the condensation temperature Tc=70 of the cold-producing medium of condenser 22 DEG C, as shown in Fig. 2 (a), in the scope of heat exchange ratio Qsc/Qc more than 0.2 but below 0.8, in the scope of the mass dryness fraction Xei of cold-producing medium that flows into evaporimeter 25 more than 0 but below 0.55, and then, as Fig. 3 (a) (b) as shown in, if in the scope of the mass dryness fraction Xei of the cold-producing medium of inflow evaporimeter 25 more than 0 but below 0.55, the cold-producing medium flowing out from supercooling heat exchanger 23 reaches supercooling state.Equally, even in the situation that adopting R410A as cold-producing medium, if under outside gas temperature AT=-25 DEG C, the condition of condensation temperature Tc=60 DEG C of the cold-producing medium of condenser 22, as Fig. 2 (b) and Fig. 4 (a) (b) as shown in, in the scope of heat exchange ratio Qsc/Qc more than 0.2 but below 0.8, the cold-producing medium flowing out from supercooling heat exchanger 23 reaches supercooling state.Therefore, in the present embodiment, specified the heat-conducting area of supercooling heat exchanger 23, so that in the scope of heat exchange ratio Qsc/Qc more than 0.2 but below 0.8.In addition, in Fig. 3 and Fig. 4, Pc refers to that, by the refrigerant pressure of condenser 22, Ps refers to by the pressure of the cold-producing medium of brake 25.
In preferred embodiment, supercooling heat exchanger 23 remains on the mass dryness fraction of the cold-producing medium flowing out from supercooling heat exchanger 23 more than 0.8 but when less than 1.0, has the heat-conducting area of heat exchange ratio Qsc/Qc more than 0.2 but below 0.7 in bypass flow fine jade 3.Like this, can the mass dryness fraction Xei when utilizing R410A to be used as cold-producing medium remain on more than 0 but below 0.45, the cold-producing medium flowing out from supercooling heat exchanger 23 reaches supercooling state (referring to Fig. 2 (b) and Fig. 4 (a) (b)).
The control that control device 4 carries out is described below.
As shown in Figure 1, in bypass flow path 3, be provided with temperature (inflow temperature) Tbi that detects the cold-producing medium that flows into supercooling heat exchanger 23 inlet temperature sensor 61, detect the outlet temperature sensor 62 of temperature (outflow temperature) Tbo of the cold-producing medium flowing out from supercooling heat exchanger 23.Control device 4, according to the detected value being detected by various sensors 61,62, is controlled rotating speed, the conversion of cross valve 28 and the aperture of main expansion valve 24 and bypass expansion valve 31 of compressor 21.
In the present embodiment, control device 4 in the time that routine turns round, in bypass flow path 3, control main expansion valve 24 and bypass expansion valve 31 so that the mass dryness fraction of the cold-producing medium flowing out from supercooling heat exchanger 23 more than 0.8 but less than 1.0.Now, owing to suitably having set the heat-conducting area of supercooling heat exchanger 23, therefore, heat exchange ratio Qsc/Qc reaches more than 0.2 but below 0.8.
In addition, be not limited to the heat-conducting area of supercooling heat exchanger 23, for example, pressure sensor or temperature sensor are set in condenser 22 to obtain the condensation temperature of condenser 22, at the outlet set temperature sensor of condenser 22, its temperature difference is remained on to 1～5K left and right at the supercooling degree of condenser 22 outlet sides, simultaneously, if control main expansion valve 24 and bypass expansion valve 31 so that the mass dryness fraction of the cold-producing medium flowing out from supercooling heat exchanger 23 more than 0.8 but less than 1.0, controls that heat exchange ratio Qsc/Qc reaches more than 0.2 below 0.8.
In addition, owing to passing through in bypass flow path 3, control main expansion valve 24 and bypass expansion valve 31 so that the mass dryness fraction of the cold-producing medium flowing out from supercooling heat exchanger 23 more than 0.8 but less than 1.0, thereby can guarantee to greatest extent the supercooling effect of cool-heat-exchanger 23, therefore, can expand the cold-producing medium enthalpy difference between the entrance～outlet of evaporimeter 25.Meanwhile, due to the humidity that can increase at the cold-producing medium of evaporimeter 25 entrances, therefore, the insignificant pressure loss that can suppress in evaporimeter 25 increases,, the suction pressure that can realize compressor 21 rises, and realizes the increase of refrigerant flow, the increase of condensation (heating) ability.
Specifically, control device 4 is controlled main expansion valve 24 and bypass expansion valve 31 so that flow into temperature T bi and to flow out temperature T bo roughly equal.
In addition, replace inlet temperature sensor 61, can export or between evaporimeter 25 and compressor 21, pressure sensor is set by the supercooling heat exchanger 23 in bypass flow path 3, according to the pressure being detected by this pressure sensor, in bypass flow path 3, control main expansion valve 24 and bypass expansion valve 31, so that the mass dryness fraction of the cold-producing medium flowing out from supercooling heat exchanger 23 is more than 0.8 but less than 1.0.
Specifically, can obtain saturation temperature according to the pressure being detected by pressure sensor, and control outflow temperature T bo with the temperature that reaches capacity.
Generally, due to ambient atmos temperature, AT is lower, evaporating pressure in evaporimeter 25 is just lower, therefore, the supercooling degree in supercooling heat exchanger 23 reach identical, the mass dryness fraction that flows into the cold-producing medium in evaporimeter 25 becomes large,, because the refrigerant gas composition that is unfavorable for evaporation increases, therefore, the heat absorption capacity of evaporimeter reduces.In this case, preferably control main expansion valve 24 and bypass expansion valve 31 by control device 4, so that as shown in Figure 5, AT is lower for ambient atmos temperature, and Qsc/Qc is larger for heat exchange ratio.
Like this, the supercooling degree exporting by increasing supercooling heat exchanger 23, reduction flows into the enthalpy of the cold-producing medium of evaporimeter 25, thereby compared with the situation less with heat exchange ratio Qsc/Qc, the enthalpy change amount that can expand cold-producing medium in evaporimeter 25, increases heat absorption capacity.As a result, in the time that extraneous gas temperature AT is lower, can supplements and follow the enthalpy of the cold-producing medium that flows into evaporimeter 25 to rise, the reduction of the caloric receptivity of cold-producing medium in evaporimeter 25.In addition, can for example detect ambient atmos temperature AT by outside air temperature sensor.
In addition, the condensation temperature Tc of cold-producing medium is higher, must be in the case of the enthalpy of the cold-producing medium of evaporimeter 25 entrances is identical, increase the supercooling degree that supercooling heat exchanger 23 exports, therefore,, with respect to the heat exchange amount in condenser 22, must increase the heat exchange amount of supercooling heat exchanger 23.In this case, preferably control main expansion valve 24 and bypass expansion valve 31, so that as shown in Figure 5, the condensation temperature Tc of the cold-producing medium of condenser 22 is higher, and Qsc/Qc is larger for heat exchange ratio.
Like this, can be with respect to the heat exchange amount in condenser 22, increase the heat exchange amount of supercooling heat exchanger 23, and reduce the enthalpy of the cold-producing medium of evaporimeter 25 entrances, thereby with heat exchange ratio Qsc/Qc hour compared with, the enthalpy change amount that can expand cold-producing medium in evaporimeter 25, increases heat absorption capacity.As a result, can supplement the enthalpy of following the cold-producing medium that flows into evaporimeter 25 causing because of condensation temperature Tc rising and rise, the reduction of the caloric receptivity of cold-producing medium in evaporimeter 25.
In addition, condensation temperature Tc can adopt and flow out temperature T bo.
Bypass flow path 3 needn't be between supercooling heat exchanger 23 and main expansion valve 24, from refrigerant loop 2 branches, and can be between condenser 22 and supercooling heat exchanger 23, from refrigerant loop 2 branches.
In addition, main expansion gear of the present invention and bypass expansion gear needn't be expansion valve, can adopt the decompressor by the refrigerant-recovery power expanding.In this case, for example, by the generator being connected with decompressor, make load variations, control thus the rotating speed of decompressor.
In addition, the heated fluid being heated by condenser 22 needn't be water, can be also air., the present invention is also applicable to aircondition.
Industrial Applicability
The present invention is specially adapted to by freezing cycle device heating water and in heating, utilizes the plumbing fixture of heated water.
Claims (3)
1. freezing cycle device, is characterized in that:
Be provided with:
With the refrigerant loop of loop connecting compressor, condenser, supercooling heat exchanger, main expansion gear and evaporimeter,
Bypass flow path, it is between described supercooling heat exchanger and described main expansion gear or between described condenser and described supercooling heat exchanger, from described refrigerant loop branch, and through described supercooling heat exchanger, between described evaporimeter and described compressor, be connected with described refrigerant loop; With
Be arranged on the bypass expansion gear that is positioned at described supercooling heat exchanger upstream side in described bypass flow path,
Described supercooling heat exchanger is when adjusting the aperture of described bypass expansion gear so that the mass dryness fraction of the cold-producing medium flowing out from this supercooling heat exchanger reaches more than 0.8 when less than 1.0 in described bypass flow path, in described supercooling heat exchanger by the cold-producing medium of described bypass expansion gear decompression and heat exchange amount between the cold-producing medium of described condenser outflow with respect to the ratio that flows into the heat exchange amount between cold-producing medium and the heated fluid of this condenser described condenser, be that heat exchange ratio is more than 0.2 but below 0.8
Described freezing cycle device is also provided with control device, and this control device is controlled described bypass expansion gear in described bypass flow path, the less than 1.0 so that mass dryness fraction of the cold-producing medium flowing out from described supercooling heat exchanger reaches more than 0.8,
Described freezing cycle device is also provided with:
Inlet temperature sensor, it detects the temperature of the cold-producing medium that flows into described supercooling heat exchanger in described bypass flow path; With
Outlet temperature sensor, it detects the temperature of the cold-producing medium flowing out from described supercooling heat exchanger in described bypass flow path,
Bypass expansion gear described in described control device control, so that the temperature being detected by described outlet temperature sensor is substantially equal to the temperature being detected by described inlet temperature sensor.
2. freezing cycle device according to claim 1, wherein: described condenser is the heat exchanger that makes to carry out between cold-producing medium and heated fluid heat exchange the heated fluid of heating.
3. plumbing fixture, its device for utilizing hot water of being generated by heater to heat, this device is provided with freezing cycle device that claim 2 records as described heater.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2009-231660 | 2009-10-05 | ||
| JP2009231660A JP5411643B2 (en) | 2009-10-05 | 2009-10-05 | Refrigeration cycle apparatus and hot water heater |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102032699A CN102032699A (en) | 2011-04-27 |
| CN102032699B true CN102032699B (en) | 2014-10-22 |
Family
ID=43778548
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201010539415.8A Expired - Fee Related CN102032699B (en) | 2009-10-05 | 2010-09-30 | Refrigeration cycle apparatus and hot water heater |
Country Status (3)
| Country | Link |
|---|---|
| EP (1) | EP2320164A3 (en) |
| JP (1) | JP5411643B2 (en) |
| CN (1) | CN102032699B (en) |
Families Citing this family (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2495149A (en) * | 2011-09-30 | 2013-04-03 | Arctic Circle Ltd | Refrigeration Apparatus With Subcooler |
| JP2014102030A (en) * | 2012-11-20 | 2014-06-05 | Panasonic Corp | Heat-pump hot water supply device |
| EP2765370A1 (en) | 2013-02-08 | 2014-08-13 | Panasonic Corporation | Refrigeration cycle apparatus and hot water generator provided with the same |
| JP6131741B2 (en) * | 2013-07-03 | 2017-05-24 | 富士電機株式会社 | Refrigerant circuit device |
| CN103344066A (en) * | 2013-07-15 | 2013-10-09 | 江苏七政新能源有限公司 | Bent tube type cooler |
| EP3118542B1 (en) | 2014-03-14 | 2021-05-19 | Mitsubishi Electric Corporation | Refrigerating cycle device |
| EP3023711A1 (en) * | 2014-11-20 | 2016-05-25 | Vaillant GmbH | Energy control for vapour injection |
| CN108603699A (en) * | 2015-12-08 | 2018-09-28 | 特灵国际有限公司 | High-temperature-hot-water is obtained using the heat recycled from heat source |
| CN106225273A (en) * | 2016-07-29 | 2016-12-14 | 青岛海尔特种电冰柜有限公司 | Cooling cycle system and refrigeration plant |
| EP3677855B1 (en) * | 2018-06-07 | 2023-10-18 | Panasonic Intellectual Property Management Co., Ltd. | Refrigeration cycle device and liquid heating device having the same |
| EP3859230A4 (en) * | 2018-09-25 | 2022-05-04 | Toshiba Carrier Corporation | Refrigeration cycle device |
| JP6886129B2 (en) * | 2019-03-26 | 2021-06-16 | 株式会社富士通ゼネラル | Air conditioner |
| ES2950759T3 (en) * | 2019-09-09 | 2023-10-13 | Mitsubishi Electric Corp | Outdoor unit and refrigeration cycle apparatus |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1205073A (en) * | 1996-08-14 | 1999-01-13 | 大金工业株式会社 | Air conditioner |
| JP4036288B2 (en) * | 2002-07-11 | 2008-01-23 | 株式会社日立製作所 | Air conditioner |
Family Cites Families (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6124910A (en) * | 1984-07-16 | 1986-02-03 | Toru Seki | Incinerating disposal of raw garbage |
| JPH0544675Y2 (en) * | 1988-05-19 | 1993-11-12 | ||
| JPH0814676A (en) * | 1994-06-28 | 1996-01-19 | Daikin Ind Ltd | Air conditioner |
| US6405559B1 (en) * | 1997-11-17 | 2002-06-18 | Daikin Industries, Ltd. | Refrigerating apparatus |
| JP4356146B2 (en) * | 1999-07-21 | 2009-11-04 | ダイキン工業株式会社 | Refrigeration equipment |
| KR100482539B1 (en) * | 1999-10-18 | 2005-04-14 | 다이킨 고교 가부시키가이샤 | Refrigerating device |
| JP4269323B2 (en) * | 2004-03-29 | 2009-05-27 | 三菱電機株式会社 | Heat pump water heater |
| JP4771721B2 (en) * | 2005-03-16 | 2011-09-14 | 三菱電機株式会社 | Air conditioner |
| JP2007212134A (en) * | 2007-04-11 | 2007-08-23 | Daikin Ind Ltd | Air conditioner |
-
2009
- 2009-10-05 JP JP2009231660A patent/JP5411643B2/en not_active Expired - Fee Related
-
2010
- 2010-09-30 CN CN201010539415.8A patent/CN102032699B/en not_active Expired - Fee Related
- 2010-10-04 EP EP10186449.4A patent/EP2320164A3/en not_active Withdrawn
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1205073A (en) * | 1996-08-14 | 1999-01-13 | 大金工业株式会社 | Air conditioner |
| JP4036288B2 (en) * | 2002-07-11 | 2008-01-23 | 株式会社日立製作所 | Air conditioner |
Non-Patent Citations (4)
| Title |
|---|
| JP特开2005-315558A 2005.11.10 |
| JP特开2007-212134A 2007.08.23 |
| JP特开平8-14676A 1996.01.19 |
| JP特许第4036288B2 2007.08.23 |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2011080634A (en) | 2011-04-21 |
| EP2320164A3 (en) | 2014-02-05 |
| JP5411643B2 (en) | 2014-02-12 |
| EP2320164A2 (en) | 2011-05-11 |
| CN102032699A (en) | 2011-04-27 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN102032699B (en) | Refrigeration cycle apparatus and hot water heater | |
| CN103119377B (en) | Refrigeration hot water supply apparatus and refrigeration hot water supply method | |
| CN103210264B (en) | Heat pump-type air-warming device | |
| CN102419024B (en) | Refrigeration cycle apparatus and hot-water heating apparatus | |
| CN102032698B (en) | Refrigeration cycle apparatus and hot water heater | |
| CN102734969B (en) | The hot-water central heating system of freezing cycle device and this freezing cycle device of outfit | |
| US20110016897A1 (en) | Air conditioning-hot water supply combined system | |
| CN109373497B (en) | Refrigerant quantity adjusting method, device and system of temperature adjusting equipment and air conditioner | |
| CN103983052A (en) | Refrigeration cycle apparatus and hot water generator provided with the same | |
| CN102679609A (en) | Air-cooled heat pump air conditioner | |
| CN103370584A (en) | Refrigeration cycle device and refrigeration cycle control method | |
| EP2902726B1 (en) | Combined air-conditioning and hot-water supply system | |
| CN101191679A (en) | Cooling device using non-azeotropic mixed refrigerant | |
| EP2752628A1 (en) | Supercritical cycle and heat pump hot-water supplier using same | |
| CN104969014A (en) | Refrigeration-cycle device and method for controlling refrigeration-cycle device | |
| CN105556220A (en) | Refrigeration circuit with heat recovery module | |
| CN104185766A (en) | Heat-pump-type heating device | |
| CN103836847A (en) | Refrigeration cycle apparatus and warm water producing apparatus having refrigeration cycle apparatus | |
| JP6057871B2 (en) | Heat pump system and heat pump type water heater | |
| US20090223232A1 (en) | Defrost system | |
| JP2007139244A (en) | Refrigeration device | |
| CN103105024B (en) | Refrigerating circulatory device and hot water generating device | |
| JPWO2012043297A1 (en) | Hot water system | |
| CN100535550C (en) | Automobile heat pump air conditioner system | |
| JP2002310519A (en) | Heat pump water heater |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20141022 Termination date: 20190930 |
|
| CF01 | Termination of patent right due to non-payment of annual fee |